U.S. patent number 5,139,350 [Application Number 07/271,044] was granted by the patent office on 1992-08-18 for thrust friction bearing of laminate material.
This patent grant is currently assigned to Glyco AG. Invention is credited to Ulrich Engel, Heinz Gieseler, Michael Kubert, Werner Lucchetti, Karl-Heinz Riehl.
United States Patent |
5,139,350 |
Gieseler , et al. |
August 18, 1992 |
Thrust friction bearing of laminate material
Abstract
Thrust friction bearings with bent holding lugs wherein the
holding lugs depressions are formed in the slide layer before the
bending of the lugs. In one example, one shallow groove is stamped
into an integral bracket forming a holding lug. In another example,
several depressions are formed in rows, instead of grooves. The
grooves or rows of depressions extend in a direction across the
lug, preferably lying at an angle to the axis of curvature. Thus,
when the holding lugs are formed by bending, damage to the slide
bearing material will not occur.
Inventors: |
Gieseler; Heinz
(Eltville/Rhein, DE), Riehl; Karl-Heinz
(Rimbach/Odenwald, DE), Engel; Ulrich (Bad
Schwalbach, DE), Lucchetti; Werner (Walluf,
DE), Kubert; Michael (Klein-Winternheim,
DE) |
Assignee: |
Glyco AG (Wiesbaden,
DE)
|
Family
ID: |
25861756 |
Appl.
No.: |
07/271,044 |
Filed: |
November 14, 1988 |
Foreign Application Priority Data
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Nov 13, 1987 [DE] |
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3738534 |
Oct 15, 1988 [DE] |
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3835175 |
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Current U.S.
Class: |
384/420; 384/295;
384/903 |
Current CPC
Class: |
F16C
17/04 (20130101); F16C 33/14 (20130101); F16C
35/02 (20130101); Y10S 384/903 (20130101); F16C
2220/82 (20130101) |
Current International
Class: |
F16C
33/14 (20060101); F16C 33/04 (20060101); F16C
35/02 (20060101); F16C 35/00 (20060101); F16C
17/04 (20060101); F16C 017/04 () |
Field of
Search: |
;384/420,425,295,296,903,288 ;29/149.5DP,149.5R ;72/379 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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0726897 |
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Sep 1942 |
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DE2 |
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1625626 |
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Jul 1970 |
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DE |
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2638996 |
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Mar 1978 |
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DE |
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Primary Examiner: Stodola; Daniel P.
Assistant Examiner: Bowen; P.
Attorney, Agent or Firm: Lehmann; H. Gibner Lehmann; K.
Gibner
Claims
What is claimed is:
1. A thrust friction bearing constituted of a laminate member (12)
which has a carrier layer (18) and a slide layer (17) and a bonding
zone between said layers, said member having at least one integral
bent holding lug (11) which is disposed after the layers have been
bonded to each other, at an angle with respect to the slide layer,
characterized in that said lug (11) has a depressed portion (14,
19) located intermediate the ends of the bend thereof and said
depressed portion extending completely through the slide layer
(17), and at least into the bonding zone between the slide layer
(17) and the carrier layer (18), said depressed portion having a
shape which is formed in part through displacement by compression
and flowing of material, and in part by the bending of the lug
(11).
2. A thrust friction bearing according to claim 1, wherein said lug
has a camber axis (13), characterized in that said depressed
portion constitutes a single groove (14) which extends parallel to
the camber axis (13) of the bend of the lug.
3. A thrust friction bearing according to claim 1, wherein said lug
has a camber axis (13), characterized in that said depressed
portion comprises a plurality of grooves (14) formed in the slide
layer (17) and arranged side by side parallel to each other and
parallel to the camber axis (13) of the bend of the lug.
4. A thrust friction bearing according to claim 3, characterized in
that the spacing (b) of the grooves from each other is commensurate
with the thickness of the slide layer (17).
5. A thrust friction bearing according to claim 3, characterized in
that the spacing of the grooves (14) from each other has the
relation 2a.ltoreq.b.ltoreq.10a, where a is the thickness of the
slide layer (17) and b is the groove spacing.
6. A thrust friction bearing according to claim 1, wherein said lug
has a camber axis (13), characterized in that said depressed
portion is constituted of a row of separate troughs (19) formed in
the slide layer (17), said row of troughs extending parallel to the
camber axis (13) of the bend of the lug.
7. A thrust friction bearing according to claim 6, characterized in
that the troughs (19) are of circular configuration.
8. A thrust friction bearing according to claim 7, characterized in
that the distance between the troughs (19) is at least equal to the
trough diameter (d).
9. A thrust bearing according to claim 7, characterized in that the
mutual distance between the troughs (19) is not greater than three
times the diameter of a trough.
10. A thrust friction bearing according to claim 6, characterized
in that the troughs (19) are oblong.
11. A thrust friction bearing according to claim 10, characterized
in that the longitudinal dimension of the troughs (19) extends in
the direction of the trough row.
12. A thrust friction bearing according to claim 10, characterized
in that the distance (f) between the troughs (19) in the row is a
small multiple of the transverse extent of a trough (19).
13. A thrust friction bearing according to claim 1, wherein said
lug has a camber axis (13), characterized in that said depressed
portion comprises rows of troughs (19) formed in the slide layer
(17) and arranged side by side, said rows of troughs extending
parallel to each other and to the camber axis (13) of the bend of
the lug.
14. A thrust friction bearing according to claim 1, characterized
in that the troughs (19) in adjacent rows are offset from each
other.
15. A thrust friction bearing according to claim 1, wherein said
lug has a camber axis (13), characterized in that said depressed
portion constitutes a groove (14) which extends at an angle to the
camber axis (13) of the bend of the lug.
16. A thrust friction bearing according to claim 1, wherein said
lug has a camber axis (13), characterized in that said depressed
portion is constituted of a row of separate troughs (19) formed in
the slide layer (17), the said row of troughs (19) extending at an
angle to the camber axis (13) of the bend of the lug.
17. A thrust friction bearing constituted of a laminate member (12)
which has a carrier layer (18) and a slide layer (17) and a bonding
zone (21) between said carrier layer and said slide layer, said
member having at least one integral bent holding lug (11) which is
disposed, after the layers have been bonded to each other at an
angle with respect to the slide layer, there being formed in the
bent region of the lug a rounded surface at the free side of the
said slide layer and also formed a first rounded junction face
between the said slide layer (17) and the said bonding zone (21),
and further formed a second rounded junction face between the said
bonding zone (21) and the said carrier layer (18), wherein said lug
(11) has a depressed portion (14, 19) located within said bent
region, said depressed portion (14, 19) extending through the said
rounded surface at the free side of the said slide layer, through
the said slide layer (17), through the said first rounded junction
face and extending at least into the said bonding zone (21), said
depressed portion being formed by displacement of material in both
the slide layer and the bonding zone and said depressed portion
having a shape which is formed in part by the bending of the lug
(11).
18. A thrust friction bearing constituted of a laminate member (12)
which has a carrier layer (18) and a slide layer (17) and a bonding
region (21) between the said carrier layer (18) and said slide
layer (17), said member having at least one integral bent holding
lug (11) which is disposed, after the layers have been bonded to
each other, at an angle with respect to the slide layer, there
being formed in the bent region of the lug a rounded surface at the
free side of the said slide layer (17) and also formed a first
rounded junction face between the said slide layer and the said
bonding region, and further formed a second rounded junction face
between the said bonding region and the said carrier layer, wherein
said lug (11) has a depressed portion (14, 19) located in the said
bent region, said depressed portion extending through the said
rounded surface at the free side of the slide layer (17), through
the said slide layer (17), through the said first rounded junction
face, through the said bonding region (21), and through the said
second rounded junction face and extending into the said carrier
layer (18), said depressed portion being formed by displacement of
material in the said slide layer (17) and the said bonding region
(21) and in the said carrier layer (18) and said depressed portion
having a shape which is formed in part by the bending of the lug
(11).
Description
BACKGROUND OF THE INVENTION
1. Field of the Invention
This invention relates to thrust friction bearings constituted of
laminate material which has a substrate or carrier layer and a
friction slide layer, and has at least one holding lug that is
integrally formed and is bent substantially orthogonally to the
slide layer surface. The invention also relates to methods for
making such thrust slide bearings.
2. Description of the Related Art Including Information Disclosed
under 37 CFR .sctn..sctn.1.97-1.99
For the locking of thrust friction bearings against rotation,
particularly in automatic transmissions, holding lugs are used on
the bearing elements. These may be disposed at the inside of a
bearing washer, at the outside diameter thereof, or even within the
bearing surface. Due to the high degree of bending and the
considerable forces which are applied when shaping the holding
lugs, peeling of and damage to the friction bearing material
occurs, with fissuration or even detachment of friction material.
If such a material particle becomes detached during operation of
the bearing, the proper functioning of the entire group of
components is imperiled. For this reason, holding lugs cannot be
accepted as satisfactory on certain thrust friction bearings which
have disadvantageous dimensions or material combinations.
From German Patent Publication 26 38 996 K-flange bearings are
known, which are provided at the inner circumferences with the
above-described holding lugs, bent in the direction of the bearing
axis and braced against or locked to the bearing bore. Measures for
preventing the material damage above referred to, however, are not
indicated nor are they an object of this known invention.
From German Patent Publication 16 25 626 there are known collar
friction bearings consisting of a metallic support body and running
(slide) layers of plastic, where before the collar is pressed on,
it is provided with axial slits for the formation of lobes or lugs.
The lobes of the collar are not themselves machined additionally to
prevent any material damage in bending.
German Patent 726,897 describes a method for making a
collar-bearing shell half with a steel support or carrier shell and
a slide-metal layer. Secured to the running or slide surface and to
the collar is a flat steel strip having flanges, which latter are
plated with a poured-on bronze layer. After the orthogonal bending
of the flanges, the steel strip is then bent to a semicylindrical
form. Before the bending of the flanges, the flange-bending areas
are bordered on both sides at their edges by grooves extending in
the longitudinal direction of the sheetmetal. Since the grooves do
not lie in the bend region but instead in the flat portions of the
bearing shell half and of the collar, a peeling or lifting-off of
portions of the slide layer occurs in the bend region.
SUMMARY OF THE INVENTION
It is, therefore, one object of the present invention to provide
improved measures at the holding lugs of thrust friction bearings
so as to avoid peeling or other material damage of the slide layer
during the shaping of the holding lug, and in particular during the
bending thereof. Above all, the invention aims to prevent the
possibility that material particles of the sliding layer could
detach at the bend of the holding lug during operation of
components involving the bearing.
According to the invention, this problem is solved in that, before
the bending of the holding lug, some of the friction layer is
displaced in the region where the bend is to be made in the lug,
thereby to form depressed portions which extend at least into the
bonding region between the slide layer and the carrier layer. Such
depressed portions are then included in the bend and shaped with it
during the bending step.
Due to the fact that these depressed portions are disposed in the
region of the bend of the holding lug, wherein during the bending
the greatest elongation occurs in the slide layer, there is
effectively avoided any detachment of particles of the slide layer
and all of the disadvantages connected therewith.
On the other hand, according to the invention, the slide layer, and
hence the protective covering of the carrier layer which usually
consists of steel, is still largely preserved in the region of the
holding lug.
According to a preferred form of realization of the invention, a
single groove can be provided as the said depression, said groove
extending either parallel to or else at an angle alpha with respect
to the camber axis of the bend.
The depressions in the slide layer can also be made in the form of
a plurality of grooves arranged side by side and parallel to each
other, and extending parallel to or at an angle alpha to the camber
axis of the bend. The mutual spacing b of the grooves can be
adapted to the thickness a of the sliding layer as follows:
The mutual spacing of the grooves can also be matched to the width
c of the grooves in such a way that there remains between two
adjacent grooves a web whose width e is between one and three times
the width c of the grooves, namely between 0.5 mm. and 3 mm.,
preferably 1 mm.
In another form of realization of the invention, the depressions in
the slide layer can be formed as a row of troughs arranged close
together, the row of troughs extending parallel to or at an angle
alpha to the camber axis of the bend. Also, by the provision of
such troughs a tearing-open of the slide layer when bending the
holding lugs can be effectively prevented.
The invention also provides a plurality of rows of troughs arranged
side by side in the sliding layer, the rows of troughs extending
parallel to each other and parallel to or at an angle alpha to the
camber axis of the bend. Such troughs are preferably disposed to be
as close together as possible. In this connection it has been found
to be especially advantageous to arrange the troughs whereby they
are offset with respect to each other in adjacent rows; that is,
the troughs are staggered from row to row.
The troughs can be circular. The mutual spacing of the troughs from
edge to edge of the trough should preferably be one to three times
the diameter d of the troughs, namely between 0.5 and 3 mm., and
preferably 1 mm.
According to the invention the troughs can also be made oblong, as
in the form of rhombuses, triangles or crescents, with the
longitudinal extent or dimension lying preferably in the direction
of the trough row.
The mutual distance of the troughs from edge to edge is preferably
up to three times the transverse extent of the troughs, up to 3 mm.
as a maximum and preferably 1 mm.
The angle alpha at which the groove or grooves, or respectively the
row or rows of troughs extend relative to the camber axis of the
bend can be, by the invention, an acute angle, which is chosen
preferably as follows:
By the invention, the depressions, such as groove/grooves and
trough, are to be stamped into the slide layer, preferably with
displacement of material, having a depth which depends on the
thickness of the material. The depressions can be stamped to a
depth which reaches into the bonding zone between the slide layer
and the carrier layer, without extending up to or respectively into
the carrier layer. But preferably the depressions, as grooves and
troughs, should be stamped into the carrier layer, and preferably
0.1 mm. to 0.2 mm. deep into the carrier layer.
By the provision of the impressed groove or grooves, or troughs,
the risk that the friction material might splinter, peel or chip
off is eliminated to a large extent. It has been found that there
must be at least one groove in the region of the greatest curvature
to clearly reduce danger of detachment of bearing or slide
material.
Further it has been found that, if there are several grooves, the
spacing of the impressed grooves should not be less than twice the
thickness of the bearing or slide material and not more than ten
times the bearing material thickness. The best result is obtained
at a groove distance or spacing of three times to six times the
bearing material thickness. As tests have shown, an optimum groove
spacing is about 1 mm.
An especially advantageous method, according to the invention, for
producing such thrust friction bearings is had by a manufacturing
procedure where the thrust friction bearing including the portion
intended for the holding lug is made all in one piece and as a flat
preform (blank) from a laminate material comprising a carrier layer
and a slide layer; thereafter the holding lug portion of the flat
preform (blank) is bent toward the side comprising the carrier
layer, essentially at right angles to the slide surface. This
method, according to the invention, provides that at the region of
the preform (blank) which is intended for the bend but is as yet
unbent and in the flat state, at least one depression is formed in
the slide layer side, and then the portion forming the holding lug
is bent toward the carrier layer side. In this process the bending
of the holding lug can be effected without any risk of material
splintering or peeling off. Even in the region of the bend of the
holding lug the slide layer remains securely bonded to the carrier
layer. As a result, there will be no subsequent chipping off of
parts of the slide layer in the region of the bend. In particular
there is no longer any danger that any splintering or crumbling of
parts of the slide layer could occur in the region of this bend
during use of the thrust friction bearing.
An especially advantageous variant of the method according to the
invention, that can be carried out at favorable costs, provides
that the preform (blank) is cut out of the laminate material by
punching and the depression is simultaneously applied by stamping
with displacement of material, whereupon the portion intended for
the holding lug is bent. The punching, for cutting out the preform
(blank), and the stamping of the depression can be performed in a
single joint operation. It is possible also to perform the punching
for cutting out the preform (blank) and the stamping of the
depression separately in time, with a subsequent tool.
Other features and advantages will hereinafter appear.
BRIEF DESCRIPTION OF THE DRAWINGS
Embodiment examples of the invention are explained more
specifically below with reference to the drawings, wherein:
FIG. 1 is a plan view of an annular thrust friction bearing with
two holding lugs disposed at the outer circumference; the side
surface which is shown is the slide surface.
FIG. 2 is a plan view of an annular thrust friction bearing with
holding lugs disposed at the inner circumference; the side surface
which is shown is the slide surface.
FIG. 3 is a detail of a flat blank (preform) for an annular thrust
friction bearing with the flat bracket or lug portion ready to be
bent 90.degree. to form the holding lug.
FIG. 4 is a view of a modification of the invention, in a
representation similar to that of FIG. 3.
FIG. 5 is a further modification of the invention, in a
representation similar to that of FIG. 3.
FIG. 6 is a fragmentary plan view of a half-ring-shaped detail of
annular thrust friction bearing, illustrating another form of the
invention.
FIG. 7 is a section through the bearing along the line A--A in FIG.
6.
FIG. 8 is a fragmentary plan view of a further form of realization
of the invention, in a representation similar to that of FIG.
6.
FIGS. 9, 10 and 11 are fragmentary plan views of further forms of
realization of the invention, in representations similar to that of
FIG. 6.
FIG. 12 is a fragmentary plan view of an annular thrust bearing
according to the invention, having tangential brackets or lugs.
FIG. 13 is a fragmentary plan view of an annular thrust bearing
having modified tangential brackets or lugs.
FIG. 14 is a section through a holding lug, along the line B--B of
FIG. 1, and
FIG. 15 is a section through the holding lug according to FIG. 14,
but in a preferred form of realization of the invention.
DESCRIPTION OF THE PREFERRED EMBODIMENT
In the annular thrust friction bearing 10 shown in FIG. 1, two
diametrically opposite holding lugs 11 are provided at the outer
circumference, which, prior to bending, lie in the same plane as
the flat laminate material of the annular ring or washer 12. The
holding lugs 11 are formed by bending the flat projecting portions
or tabs 15 of the blank through 90.degree., toward the carrier
layer side (away from the viewer). In the example of FIG. 2, an
annular thrust friction bearing 10 has at the inner circumference
of the bearing washer 12 two diametrically opposite holding lugs
11, which, too, have been formed by bending tabs or projections
which at first lie in the plane of the washer. As FIGS. 1 and 2
show, the holding lugs 11 have shallow grooves 14 extending across
the full width of the lugs and which, in the examples of FIGS. 1
and 2, extend parallel to the axis of curvature 13.
In FIG. 3 there is shown a detail of a portion of a washer blank 12
for an annular thrust friction bearing, illustrating a tab 15 to be
bent 90.degree. for the formation of a holding lug. In this example
a shallow groove 14 is disposed parallel to the axis of curvature
13 in the region of greatest elongation (stretch) of the slide
layer. Instead of the groove 14, a row (series) of troughs (not
shown in FIG. 3) can be provided
As has been found in tests, however, this groove or these grooves
14 will be still more effective if they extend at an acute angle
alpha relative to the axis of curvature 13. As shown in FIGS. 4 and
5, when producing a flat blank for a thrust friction bearing 10
there must be formed firstly tabs or projections 15 lying in the
plane of the washer 12, into which tabs according to FIGS. 4 and 5,
grooves 14 or respectively troughs 19 are stamped. The grooves 14
or respectively the rows of troughs 19 extend at an angle with
respect to the camber axis of curvature. For the angle alpha there
applies the relation 1.5.degree..ltoreq.alpha.ltoreq.25.degree.,
preferably 2.degree..ltoreq.alpha.ltoreq.18.degree., the preferred
angle alpha is 3.degree..
In the example of FIG. 4, the grooves 14 are formed so that they
have a notch width of c, and between adjacent grooves 14 a web 16
remains whose width e from groove edge to groove edge is about one
to three times the groove width c. Advantageously the web width e
is about 0.5 to 3 mm., preferably approximately 1 mm.
The distance b between adjacent grooves 14, measured from center to
center, is, in the example according to FIG. 4, matched to the
thickness of the slide layer 17. For the groove spacing b relative
to the thickness a of the slide layer 17 there applies:
The optimum is a groove spacing b of about 1.5 to 3 mm.
In the example of FIG. 5, instead of grooves, rows of troughs 19
are stamped into the bracket 15 as depressions. As FIG. 5 shows,
these trough rows extend along lines which run at an acute angle
alpha to the camber axis of curvature 13. The impressed troughs 19
are staggered from row to row, i.e. the troughs 19 of one row are
opposite the interstices between the troughs 19 of the adjacent
row. In this way an almost uniform distance f to the next trough
(in the same row or an adjacent row) is had all around the edge of
a trough 19. The trough distance f should be between one to three
times the trough diameter d, optimally about 0.5 to 3 mm., and
preferably 1 mm.
FIG. 6 shows a half-ring-shaped detail of the blank (preform) of a
bearing washer 12, the troughs 19 in the tab 15 being arranged in
parallel rows to the axis of curvature 13. As FIG. 7 shows, the
troughs 19 are formed as conical depressions. FIG. 8 shows a tab 15
likewise provided with troughs 19, which tab is located at the
inner circumference of the bearing washer 12.
In FIG. 9, the depressions are formed as rhombuses 22, and in FIG.
10 as triangles 23.
As shown in FIG. 11, the rhombuses 22 are arranged in rows which
form, with the axis of curvature 13, the angle alpha.
FIGS. 12 and 13 show blanks (preforms) of a bearing washer 12 with
tangential tabs 15, into which again depressions are stamped. In
the case of FIG. 12, these depressions are formed as troughs 19,
and in the case of FIG. 13, as a groove 14 in each instance.
In the illustrated examples the grooves 14 and the troughs 19 are
formed by stamping in the slide layer 17, accompanied by a
displacement of material. As FIG. 14 shows, the depth of the
grooves 14 and correspondingly also the depth of the troughs 19
should extend at least into the bonding zone 21. However, it has
been found that it is still more favorable to stamp the grooves 14
or respectively the troughs 19 still deeper, namely 0.1 to 0.2 mm.
deep into the carrier layer 18 (see FIG. 15). As particularly
illustrated in FIG. 14, there is formed in the bent region of the
lug, a rounded surface at the free side of the slide layer, and
there is also formed a rounded junction face between the slide
layer and the bonding zone. There is further formed a second
rounded junction face between the bonding zone and the carrier
layer.
In all embodiments of the invention the depressions, be they
grooves 14 or troughs 19, which are to be stamped are accompanied
by displacement of material. As against forming the depressions by
chip-removal machining, this offers not only price advantages, but
above all also the assurance that no chips of material will form
which could adhere to the workpiece. Lastly, by the stamping-in of
the, depressions, be they grooves 14 or troughs 19, an additional
compaction or compression and flowing of material occurs and
strengthening in the bonding region 21 between the slide layer 17
and the carrier layer 18 is brought about, so that also due to this
the slide layer 17 has less tendency to detach from the carrier
layer 18 during the bending, as compared with applying the
depressions by chipping machining.
Variations and modifications are possible without departing from
the spirit of the invention.
Each and every one of the appended claims defines an aspect of the
invention which is separate and distinct from all others, and
accordingly it is intended that each claim be treated in this
manner when examined in the light of the prior art devices in any
determination of novelty or validity.
* * * * *